Grade crossing gate



NOV. 14; 1944. M K 2,362,710

GRADE CROSSING GATE Filed April 21, 1941 7 Sheets-Sheet 1 Nov. 14,' 1944. 4 s. MISKELLY GRADE CRQSSING GATE 4 Filed April 21. 1941 7 Sheets-Shee t 2 s. MISKELLY GRADE CROSSING GATE Filed A pril 21. 1941 Nov. 14, 1944.

'7 Sheets-Sheet :5

Nov. 14,- 1944.

s. MISKELLY emn'cnossmq GATE Filed April 21, 1941 7 sheets-sheet 4 f I J N 9 4 s. MISKELLY 2,362,710

GRADE cnossme GATE I Filed April 21, 1941 7 Sheets-Sheet 5 Q 8% a q NOVQ14, 1944. s E Y I 2,362,710

GRADE cR ssING GATE Filed Api'il 21, 1941 Nov. 14, 1944.

5. MISKELLY GRADE CROSSING GATE Filed April 21, 1941 7 Sheets-Sheet 7 Patented Nov. 14,

UNITED STA'lES P TENT OFFICE 'Samuel mitgfifrrgfvgfif assigm to V v Western Railroad Supply Company, Chicago,

Application April 21, 1941, Serial No. 389,541

' (cuss-7) I 9 Claims. The present invention relates to railroad grade crossing gates and more particularly to a new and novel grade crossing gate-actuating mechanism which is so constructed and arranged as to provide positive performance under all operating conditions and which'is of great simplicity.

The grade crossing gate located at the intersection of the railroad and the highway plays an important part in American life today. Upon it reliance is placed by travelers both upon the railroad and upon the highway. Such gates must be reliable in that they must be positive acting under all conditions. It is not suflicient that these gates perform their warning and life-protecting function when conditions are most favorable, but rather it is necessary and to a higher degree that they perform their function under adverse conditions. It is to a gate which is so characterized that the present invention is directed.- A gate which will move positively to both the raised and the loweredpositions against the opposition of adverse winds and under the added loads of collected ice. Its electric circuit is rela tively simple, in fact simpler than many gates which donot incorporate its advantageous characteristics.

It is an object of the present invention to provide a new and improved grade crossing gate. It is another object of the present invention to provide a new and improved grade crossing gate-, actuating mechanism. It is a still further object of the invention to provide a new and improved actuating mechanism for grade crossing gateswhich is positive in its action both when raising and lowering the gate arms. Still another object of the invention is to provide a rugged, dependable grade crossing gate including armcounterbalancing means, the lowering torque being a maximum with the gate in the clear position. A still further object of the invention is to provide a grade crossing gate in which the gate is power driven in' its downward direction, the driving means includingantomatic means to prevent an excessive speed of arm movement. A still further object of the invention is to provide a grade erasing gate in which the gate arm is motor-driven to the clear position, and is moved to the closed position by a driving motor and by gravity,'automatic centrifugally operating braking means being provided to prevent excessive 50 lowering speed. A still furtherobject of. the in- These and other more specific objects will appear upon reading the, following specification and claimsand upon considering in connection therewith the attached drawings to which they relate.

Referring now to the drawings in which a actuating mechanism upon the line 3-3 of Figure 1; r Figure 4 is a vertical section through the gateactuatingmechanism upon the line 44 of Figure 3;

Figure 5 is a vertical section upon the line 5-5 of Figure 3 and illustrates the gears connecting the motor shaft to the gate arm shaft, and also the resilient stops which determine the clear and closed positions;

Figure 6 is a section through the slot, motor, and centrifugal brake which are illustrated in side elevation with other parts in Figure 3;

Figure 7 is an end view of the slot mechanism inside the slot casing as seen from the line 1-1 of Figure 6;

Figure 8 is an end view of the centrifugal brake looking in the direction of the arrows upon the line 8-8 of Figure 6;

Figure. 9 is a diagrammatic showing of the electrical circuit of the gate-actuating mechanism and-its connection to the track relay.

Referring now to Figures 1 andzin partic lar, a complete grade crossing gate constructed 'in accordance with the presentinvention is illus trated. 'A mast I having a base! securely fastened on a. concretetoundaiion. The mast 'supportsandean'iesawamingsignofacommon vention' is to provide a grade crossing gate in which the electrical connections of the gate-operiiretembi are Aseoond refer-meeclnnctericarfiesanindicationoftheninnherottnctsgnnrm edbythegamandinthemesuitimtlmerends 2 track.- Cross arms 1 and 8 carry the usual words Railroad crossing formed of letters 5 which are also preferably of light-reflecting elements. Flashing lights I are secured suitably to the mast I by means I I and in compliance with preferred design include hoods l2 and background discs i3.

The main housing of the gate-actuating mechanism is carried by the mast I at about four feet above the base thereof and is. fixedly and securely positioned thereon as by securing means l6. Housing l contains the entire actuating mechanism of the gate arms which will be hereinafter fully disclosed, but referring particularly to Figures 1 and 2 it is seen that the gate-arm-supporting shaft I'l extends laterally through and from the sides of the housing l5 and supports .the lower extremities of a gate arm I8. One side of the gate arm I8 is extended a short distance beyond the pivotal axis comprising the shaft I1 and there carries a counterbalancing weight I5. The latter is seen to be positioned substantially directly below the pivotal'axis I! with the gate arm in the Vertical or clear" position as illustrated in Figure 1. The weight-carrying end of the gate arm, which may be referred to as the heel, adjustably supports the counterbalancing weight 19 so that the latter may be moved manuspaced from the driven housing 44; and friction ally toward or from the pivoting axis I! in order that it can exert a greater ora lesser counterbalancing force upon the arm. The manually operable locking means which permit of this weight adjustment are indicated generally by the reference character 20, and may be of any desired well known type. It is noted that the gate arm l8 carries suitable flashing lights 2| which may be of any desired type and which may be operated in any preferred manner.

As previousl stated, the gate-actuating mechanism is positioned within the housing I5 and the latter is provided with a cover 23 which may be pivoted manually to an open position upon its supporting means 24 by the use of the handle 25 provided for that purpose. Upon opening the housing l5 by pivoting downwardly the cover 23,

- the gate arm-actuating mechanism is exposed and is as illustrated in Figure 3 with the exception that certain parts are there shown in section. This structure, and the details comprising it, are disclosed in detail in Figures 3 to 8, inclusive, which are now to be discussed with particularity.

The gate arm shaft I1 is seen to be rotatably mounted within bearings the housings 21 of which are carried by the side walls of the housing I5. To drive the gate arms up and down positively through rotating the shaft [1, there is provided a driving motor which is indicated generally by the reference character 29. Motor 29 includes a stator 30 and an armature 3| 'whichis rotatably mounted upon a motor shaft 32 extended substantially parallel to the gate arm shaft I1. As is-best illustrated in Figures 3 and 5,

the driving motor shaft 32 is connected to the driven gate arm shaft II through a plurality of pinions and, gears which effect a reduction in the a toothed right angle sector or quadrant which is fixed rigidly to and is rotatable with the gate arm shaft l1.

Sector 40 is formed at its extremities with reinforced abutment surfaces, indicated generally at 41, for a parent.

While it was stated that the first driving pinion 33 was mounted on the motor shaft 32 and actuated thereby, in fact-the drive therebetweenis through an overload clutch 43 which is most clearly illustrated in Figure 6. This clutch comprises an enclosing housing 44 fixedly secured to and rotatable with the'pinion 33 and which may be formed integrally therewith; a driving plate 45 which is keyed to the shaft 42 and which is plates 46, of which there may be a plurality, which are interposed therebetween. Driving plate 45, while keyed to motor shaft 32, is in fact longitudinally slidable thereon and is spring urged so as to compress the friction plate 45 against the driven housing 44 by means of an encircling coil spring 41 which abuts thereagainst at is inner end and against an abutment 48 at its outer end which is held in position by a nut 49 screw threaded onto the end of the motor shaft. Obviously the construction provides an overload release clutch the characteristics of which are determined by the pressure exerted by the spiral spring 41 which in turn is controlled by the manually operable abutment element and nut 48 and 49, respectively.

A centrifugal brake, indicated generally by the reference character 50, is positioned immediately adjacent the overload clutch 43 and comprises a fixed enclosing drum 5| which is secured to a bracket 52 which in turn is fixedly carried by the wall 53 within the mechanism housing l-5. The inner wall surface of. drum 5| is smooth and is adapted to act as the brake surface for a pair of centrifugally operated brake shoes 55. Shoes 55 carry brake shoe linings 56 along their outer surfaces, which are curved to conform to the inner surface of the drum 5|, and each shoe is pivotally mounted near one of its ends upona pin 51. Each pin 51 is fixedly carried by a plate 58 upon a cylindrical sleeve 59 which is concentric with the clutch-tensioning spring 41. Sleeve 59 is fixedly secured by screws to the drive plate 45 of the-overload clutch. As distinguished from the pin-carrying plate 58. which is relatively loosely mounted upon the carrying sleeve 59,

there is provided immediately adjacent thereto its longitudinal position, a second sleeve 60 which speed of the gate arm shaft relative to the speed of the motor shaft. Referring to Fi ure 5 in particular, it is seen that the motor shaft '32 carries a pinion 33 which meshes with a gear 34 which is rotatably-mounted upon a shaft 35 and which is fixedly connected to a second pinion gear 36. A second driven gear 31 meshes with the second pinion gear and is driven thereby and is itself car riedbya supporting shaft 38'." Fixed to and rotating with the second driven'gear 31 is a third is driven or sweated upon its supporting sleeve 59 so as to be fixed and non-rotatable thereon. Sleeve 50 is formed at diametrically spaced points with radially extending driving abutments or stops 6| which are rounded at their outer extremities. Each of these stops, when the sleeve 60 is advanced in a clockwise direction as viewed in Figure 8, the gate-raising direction, is adapted to contact a cam end 52 of the adjacent brake shoe 55, and to cam that end outwardly so as to move the main body of the brake shoe radially inwardly from contact. with the drum 58, the abutment finally seating against the seat 53 formed on the brake shoe to receive it. Upon the opposite side of each drivingabutment 6| from the cam end 52 is'positioned a pin 65 carried by the plate which also carries the brake shoes 55. In the gate-lowering or counter-clockwise purpose hereinafter to become aprotation of the motor shaft, and so of the abut ment elements GI (reference being had again to Figure 8), each of these elements moves from under the end of ,the adjacent brake shoe 55 and contacts the pin 65 to cause the rotation of thethe motor to drive the gatearms upwardly and downwardly under the predetermined conditions which are hereinafter discussed, and which incidentally reverses the direction of rotation of the. driving motor 29, comprises generally: (1) a slot 68, which includes certain hold clear magnets. and certaincontacts; and (2) a plurality of contacts which are positioned and operated by con-' troller cams mounted directly upon the gate arm shaft II. These latter contacts and their controllers will now be discussed.

Referring now to Figures'3. and 4 in particular,

two parallel insulator mountings I0 and II are contacts 80, 8I and 82 in the desired sequence I and when the gate arm is in certain positions, as will hereinafter be fully explained.

Turning now to the slot, indicated generally by the reference character 68', this device isseen to be positioned immediately adjacent the driving motor 29 upon the opposite side thereof from the overload clutch 43 and also the centrifugal brake mechanism 50. A primary function of the slot is to secure the gate arms I8 in the open or clear position when the track section which controls the gate is clear} This'primary functionis ac-- complished by the provision of a ratchet gear, I02 which is mounted upon and rotatable with the extended end of the motor shaft 32. ,Cooperating with the rotatable ratchet I02 is the looking or retaining pawl I03 which is pivotally mounted at I04 so as to be angularly movable between two stop pins I05 and I06, there being a spiral spring I0'I providedwhich positions the pawl I03 substantially centrally. between the two stop pins and which resiliently opposes its movement in the direction of the pin I06. The pawl I03 and its pivot point is carried by a relatively heavy locking arm I08 which is pivotally mounted at I09 upon a e bracket I IILfixed to the rear wall of the slot cas seen toextend substantially parallel to the shaft I I1. Spaces are provided on each for a multiplicity of binding posts and contaets and in the commercial embodiment as many of these may be provided as is necessary to operate bells, re

lays, etc but for the purposes of the present invention, and for the controlling of the-gateactuating mechanism, ther is need but for three pairs of these. The stationary contacts are shown carried by the upper insulator mounting I0 and are indicated by the reference. characters I2, I3 and-I4, and from these extend leads I5, I6 and 11, respectively. The movable contacts which are adapted to make contact with stationary coning. Pawl-carrying arm I08 is a weighted ele-.

ment which tends under the force of'gravity to 'fallfrom the ratchet wheel I02 to a lower position in which the pawl I03 just clears the ends of the teeth of ratchet I02; At the outer or forward end of pawl-carrying arm I08'is an L-shaped armature bar II2 pivoted at H3 and carrying a pin at its upper end, as indicatedat II 4, which pin supports the arm I08 through slidingly seating in a slot II5 formed therein. As is perhaps best illustratedin Figure 6, the pawl-carrying.

arm I08 is in fact a pair of arms as is' the upper tacts I2, I3 and I4, respectively, are indicated by the reference characters 00, 0| and 02 and from them extend, leads 83, 84.and 85, respec- 4 tively. Each movable contact carries near its midpoint an insulated abutment element, indicated generally by the referencecharacter B],

which is adapted to be contacted by a controller cam carried by the adjacent gate arm shaft I'I end of the, armature bar I I2.' At its lower end,

however, the armature bar II 2 is a plate-like element which is connected to the armature proper II I. p

The pivotal movement of the armatur bar H2, ended the raising and lowering of the pawlcarrying arm I08, is accomplished by the movement of the armature III toward and from the in certain positions of the latter for the purpose of establishing or breaking the contact between each pair of contacts. It is clear that by suitably relating the controller cam relative tothe gate arm shaft I1 the individual pairs ofcontacts can be opened and closed as desired with respect to each other and to the angular ate arms. i

The controller cams carried by the gate arm shaft I1 and adapted to position the movable contact elements 80, 8| and 82, are indicated respectively by the'refe'rence characters 90, 9| and 32. Each controller cam'comprises body sections 94 and 95, thelatter including thecam proper indicated at" 96. Sections 94 and 95 are interconnected by a pair of parallel screws 98 and 90,

the former comprising an adjusting screw, which cooperates with a spiral threaded groove I00 formed in the shaft I'I immediatelythereunder,

while the second screw 99 is adapted. to clamp the two body portions together when the adjustposition ofthe I magnetic pole face- II I which extends adjacent and parallel thereto. The pole face I I7 carries a core, as lndicated at I I8,'-' and is adapted to be magnetized by one or both' of a plurality of coils indicated at I19 and I20, respectively. The coils H9 and may have dividedwindings which indicated by the referencecharacter I20. either event the high resistance coil is adapted have high and low resistance characteristics, or one coil may be a high resistance coil and the other .a'low resistance coil; The low resistance coil in the present example will be illustrated by the coil IIO, while the'high resistance coil will be In to consume a lesser amount of current and to perform the function of an armature-holding coil, while the second low resistance coil performs the function of anactuating coiland is more powerful as it draws a greater current. The

armature arm II2-at its lower end has a move- I menttoward and from the pole face I, together with the armature III, which is substantially one quarter inch in extent and which is controlled by an adjustable stop screw indicated generally by the reference character I22 and which includes a locking nut I23. .A pair of, coil springs I25, en-

ment bymeans of the adjusting screw 98 has been properly made. 'The cam controllers 90, 0| and circling armature-carried headed bolts I26, are

..positioned at the opposite ends of the armature 92 are so positioned angularly relative to the gate arm shaft I1 as to open and close the movable bar I I2 and contact the outer face thereof, These springs serve as resilient buffers and take-ups and for the mechanisms operation. The operation not only limit the force exerted by the armature I I I on the pawl I03 in holding the latter in looking position, but also acts as a shock absorber to absorb the shock when the heavypawl-carrying arm I08 falls from its locking position under the force of gravity,

This construction of the slot to perform its primary locking function is seen, then, to com-' prise a rotatable ratchet wheel I02 which is adapted to be locked in various positions by a pivoted pawl I03, the position of which is controlled by a pair of hold clear coils II9'and I20, one of which is a low resistance high-currentconsuming actuating coil and the other of which is a high resistance low-current-consuming holding coil. Additionally, the curvatureof the teeth of the ratchet I02 and the shape and position of the pawl I03 are such that with the pawl-carrying arm I in its upper position and the pawl I03 in I contact with the ratchet teeth,- the ratchet wheel will be locked from -rotation in a. clockwise direction, as seen in Figure '1, but a tendency to move in the counter-clockwise direction will result in the pivotal movement of the pawl I03 to thestop I06, the pawl being so shaped that the ratchet teeth can then pass thereover.

In addition to its primary function of locking in position the motorshaft 32, and so the gate arm insulator mountings I35 and I36 carried by that bracket. connected to these front and back contacts as of the construction is much improved, however, by the presence of bumper elements which absorb the shock incident to the gate reaching the end of its movement. Reference to Figures 4 and 5 disclose that above and below the gate arm shaft I1, and positioned so as to be abutted by the reinforced portions 4I upon the toothed quadrant 40, are a pair of spring-held abutment pins I43. These pins are screw threaded into the flanged sleeve I 44 which seats lidingly in a socket I45 formed in the side wall of the mechanism I casing I5. A coiled spiral spring I46 abuts the Y outer wall of the socket I45 and at its inner end abuts the head or flange of the sleeve I44 and urges that element, together with the abutment pin I43 screw threaded therein, in the direction of the interior of the mechanism casing 23. The position of the head of pin I43 is determined by its position in the sleeve I44 and by a positioning nut I41 which is screw threaded upon its projecting outer end outside of the socket I45. A screw-held detachable protecting cap I encloses and protects the adjustment nut I41.

The abutment pins I43- are so positioned relative to the arcuate'sector 40 that immediately prior to the gate arm reaching its upper or clear position the upper abutment surface M will contact the upper abutment pin I43. With the gate arm moving to its lower position the lower abutment' surface 4| will contact the lower pin I43 Just prior to reaching that position, and remains in contact as is clearly illustrated in Figure 5. When contacted a pin I43, together with its sleeve I44, is forced outwardly against the resisting force of the spring I46 by the gate arm momentum and in opposing each movement reduces the shock ofstopping the gate in its final position. I The strength of the spring I46 and the position Suitable current-conducting leads .are I will hereinafter beset forth. Attention is directed to the fact that each front and back contact includes a spring strip which positions it for slight displacement forwardly or rearwardly of the slot.

Preferably the frontcontacts I28 and I3I are of selectively with front and back stationary contacts I28 and I29, while the second movable contact I40 is adapted to make selective contact with stationary front and back contacts I3I and I32.

As movable contacts I39 and I40 move with thearmature bar II2, it is clear that they will make simultaneous contact with the front contacts or with the two rear contacts.

From the foregoing it is clear that when the armature I I I is drawn against pole face I I1 upon the actuating hold clear coils I I9 being energized, that movable contacts I39 and I40 will mak contact with the front contacts I28 and 'I3I. It is also clear that with the hold clear coils deenergized and the pawl-carrying arm I08 in its lower position, and therefore with the armature III spaced from the pole face II1, that the movable contacts I39, I40 will make contact with the back contacts I29 and I32.

The. foregoing substantially completes the mechanism which raises and lowers the gates, hold them in given positions, and opens and of the pin I43 are so adjusted as to absorb all of tne shock.

Turning now to Figure 9 in particular, the electrical circuit of applicants device and its relationship to the controlling track and track relay is cleariy illustrated.' In the diagrammatic circuit illustrated a track comprising rails I50 is divided into an insulated section by insulators closes the various contacts which are necessary 76 I5I. Across this track section is a battery B and a track relay I52 having a movable contact The front contact I54 of the track relay is directly connected to line while to the movable contact I53 is connected a lead I56 which divides into conductors I51 and I58 which connect to the low resistance actuating coil H9 and the high resistance coil-holding I20, respectively. From the former a lead I59 extends to stationary contact 12 which is one of the contacts controlled by the gate arm shaft I1 as above described. From the high resistance hold clear coil I20 a conductor I60 extends directly to the op posite side of the incoming power line. It is clear then that this latter high resistance'hold clear coilwill at all times be energized with the track relay picked up, that is, at all times when the: track is in the clear condition. A lead I6I connects the movable contact 80, which cooperates with stationary contact 12, directly to the opposite side of the incoming power line and so it is clear that the current will pass through the actuating low resistance hold cl'ear coil I I9 whenever both the track relay and the contacts 12 and are closed. The controller cam which controls the opening and closing of contacts 12 and 80 by directly positioning contact 80, is so positioned relative to the gate arm shaft I1 that contacts 12 and 80 are closed with the gate arm between and 88 and are open at 88 to 90,

the latter being the vertical position. This deenergization of the actuating low resistance .coil II9 between 0 and 88 is desirable in 'that'when I the gate arm is in the vertical position and the ratchet-locking pawl I03 is in operative locking position relative to the ratchet I02, the armature I II having been moved magnetically to its position adja'cent-the pole face III, the magnetic force required to hold'the parts is less than the 'force required to initiate the movement to that position, and the assistance of the coil I I9 is not required. The strength of'the high resistance holding coil is suificient to maintain the locking position whereas it might be 'insuflicient to accomplish the movement of-the parts to that position in the first place. v

The movable contact I39, which is actuated by the hold clear coils H9 and I20, is seen to be close them between 45 and 90.

connected by a conductor I63 to the positive incoining current source and is adapted to make and back contacts I 28 and I29. Front. contact 7 I28 is connected by conductor I64 directly to-the stationary contact 13 controlled by the gate shaft I1 while the back contact I29 has a common 'connection with the front contact I3I and,

side of the motor armature. Also it is clear that when the hold clear coils are de-energized and the movable contact I39 is in its de-energized position, in whichit makes contact with back contact-'l29, that a connection is made therethrough and through the lead I65 from the positive side of the incoming line to the opposite side of the armature. In other words, the movement of the contact I39 reverses the connection of the positive side of the incoming current to the motor armature 3|. The controller cam 9i upon the gate arm shaft I1 is so positioned angularly that contacts 13 and M are closed between 0 and 88 and open between 88 and 90, exactly as in the case of contacts Hand 80.

The second movable slot-controlled contact I40 is seento be-connected at its heel by a conductor contact, as previously described, between front I by the slot.

I10 to one side of the motor field 30, the opposite side of the field being connected by a conductor I1I to the negative side of the current source. Movable-contact I 40 is adapted to makecontact with front contact I3I or back contact I32, as

described above, and when inits energized posir tion and in contact with the latter conducts cur rent from the negative current source which has passed through the motor field 30 directly to one side-of the motor armature 3I; When thecontact I 40 is in this position, it is to be noted, the first movable slot contact I39 is connected to the opposite side of the 'motor through contact I28, lead I 64, and gate-arm-controlled contacts 13 and 8|, the closed position of the latter being assumed.. With the movable slot-controlled contact I 40 in its down or' tie-energized position it makes contact'with back contact I32 which is directly connected by means of a conductor I 13 ,to the movable contact 82 actuated and controlled by the gate armushaft. Cooperating contact 14, which is adapted to be engaged by contact 82, is connected through a conductor I12 to the conductor I68 and by the latter to one side of the motor armature 3|. 'When the slot controlled contact I40 is in this second and de-energized position it is to be noted that the. other slot-controlled contact I39 has moved into contact with back contact I29 and that current from the positive source is conducted to the opposite side of the motor through the lead I65. Controller cam 92 carried by the gate arm shaft is so positioned and contoured as to open contacts 14 and 82 between 0 and 45 and to When contacts 14 and 82 are closed and the slot-controlled contacts I39 and I40 are in their de-energized positions, the motor is rotating ina direction to drive 'In the track clear condition the track relay I52 is energized and the contacts I53 and I54 are closed. 'Energy passes through the holding coil I20 and the ratchet-locking pawl I03 is held in its upper locking position and the clockwise rotation of the motorshaft 32 (as viewed in Figure '1), which would result in, a lowering of the gate, is prevented. The gate is then held in the .vertical position and no current passes through the actuating hold clear coil H9; the contacts 12 and being open, their closed range being 0? to 88. Contacts 13 and 8I, having the same range, are also open and current cannot pass to the motor from that source. Contacts 14 and 82 are closed but no current to the motor can pass therethrough as the sole possible source of incoming current, comprising the lead I13, connects to the contact I32 which is open. In this relationship, it is seen, therefore, that the gate arm is inthe vertical position and is retained there Upon a train entering the insulated track section, formed by the rails I50, the track relay I52 7 is shorted and contact I53 falls from contact I 54. The slothold clear coils II 9 and I20 are immediately de-energized and the pawl arm I08 carrying the locking pawl I03 falls permitting the motor shaft 32 to rotate in a clockwise direction, as viewed in Figures 1 and '7, and the gate arm moves downward. The falling of the pawl-carrying arm I08 pivots the armature bar [I2 counterclockwise about its pivot point II3, as viewed in Figure 7, and with the bar the slot-actuated contacts I39and I40 move from'their front contacts I28 and I3I to their back contacts I29 and I32. Current then flows from the positive source through the contacts I39 and I29, the lead I65 to one side of the motor, and from the other side of the motor through the leads I68, I 12 to the closed contacts 14 and 82' (closed range=90 to 45) and therefrom through the lead I13 to the back contact I32 from whence it passes through the movable slot contact I40 to the lead I10,

through the motor field 30, and then by the lead III back tothe negative side of the line. When so connected the motor drives the gate arm down and this operation continues until the contacts I4 and 82 are opened when the gate arm reaches the selected angular position which is between 45 and 5 preferably. Thereafter the downward movement of the gate continues under gravity and by virtue of its own momentum. As the gate arm moves downward the net torque due to gravity acting upon the gate arm is reduced by gravity acting upon the counterbalance weights I9, and constantly decreases, it having been a maximum with the gate in the clear position, in which the counterbalancing weight I9 had a zero lever arm, and it being a minimum with the gate in substantially the horizontal position. This decrease in the downward torque due to gravity is due to the fact that the center of gravity of the counterbalancing weight I9 increases its lever arm from zero to a maximum whereas the gate arm center of gravity has an initial lever arm and does not increase in the same proportion.

As the gate approaches the end of its movement the lower shock-absorbin abutment pin I43 is contacted by the sector 40 and the gate is eased to its final horizontal position. The pairs of contacts I2, 80 and I3, 8| respectively, are closed, in fact have been closed since the gate arm moved downwardly past 88 from the horizontal, but no current passes therethrough or to the motor. This is so for pair I3, BIfor with the slot de-energized its contacts I39, I28 are open. As to pair 12,00, the opening of the track relay I52 caused its movable contact I53 to move to open'position thereby cutting oiT circuit from both hold clear coils H9 and I20 and so from contacts 12, 80 which'are in series with coil II9. v

As long as the train remains in the insulated track section the relationship just described con tin'ues and the. motor remains de-energized as.

do the hold clear coils H9 and I20.

Upon the train passing from the insulated track section the track relay I52 is again ener gized and movable contact I53picks up and contacts front contact I54, whereupon hold clear coils 'I I 9 and I20 are energized and the pawl I03 ance actuating hold clear coil II9 is-cut off, the

current continuing to pass through the high reof speed, due either to the wind blowing behind the gate to force it downwardly, or to the presence of collected ice which increasesthe weight of the gate arm. fro-prevent an excessive lowering speed under these and other'conditions the centrifugal brake 50 was provided. Whenv the motor is driving the arms upwardly, the direction of rotation of the motor shaft 32 is such that each of'the abutment elements 6| on the sleeve 60, which sleeve is at all times fixed relative to centrifugally against drum 5|. The friction be tween the brakeshoes 55, and more particularly I ing speed.

is moved by its carrying arm I08 to its upper or ratchet-locking position. As described, however, the pawl shape and position are so related to the ratchet and its teeth that the movement of the ratchet in a counter-clockwise direction, as viewed in Figure '7, is not prevented and when the motor shaft- 32 is moving in that direction the gate arm is being raised. Also, as a result of the energization of the hold clear coils, H9 and I 20, the movable contacts I39 and I40 are moved from their back contacts I29 and I32 and into contact with their front contacts I28 and I3I. Immediately current passes from the positive source through contact I39, lead I64 to the closed contactsi'l3, 8|, and from there through conductors I61 and I68 to one side of the motor time contacts 13 and 8| break and current to the motor is.cut off. At the same time contacts 12 and 80 open and current through the low resistthe shaft, forces itself under the adjacent cam end 62 of the brake shoe 55, and moves those elements inwardly so that it can perform no braking action against the enclosing drum 5|. With the motor shaft rotating in the opposite direction upon the gate arm being lowered, however, the abutment element 6| moves from under the cam end 62 andcontacts the adjacent pin 65. In this relationship the brake shoes 55 are free to fly outwardly under centrifugal force and should the arms move downwardly at excessive speed, the motor shaft would also rotate at an excessive speed and the shoes 55 would be thrown between the brake lining 56 and the drum, provides a load which brakes and retards the lower- Should anything obstruct the movement of the gate arm in either direction the shearing and breaking of a geafor pinion is prevented through the provision of the overload clutch 43 in which the tension upon the spring 41 determines the force required to make the clutch slip and should be so adjusted thatrelative movement will take place between'the two .parts of the clutch, that is parts 44 and 45, before a load point has been reached which could result in the breakage of any gear or pinion.

I claim": v

1. In a railroad crossing signal, a gate arm pivoted about an horizontal axis, counterbalancing means connected to said arm and arranged as toexert a greater counterbalancing force with the arm in the warning" position and a minimum force with the arm in the clear position, an actuating mechanism geared to said arm and including a reversible electric motor and an electric circuit to pass current through said motor in opposite directions "in different angular'positions ofsaid arm, and a centrifugal brake connected to the motor shaft and operative above a predetermined speed to limit the speed of move ment-of said gate arm in one direction only.

1.2.111 a railroad highway crossing gate, a gate arm, a gate-arm-actuating mechanism comprising a reversible driving motor connected to said arm for up and-down propulsion, a centrifugal brake connected to the shaft of said motor at one side thereof, and an overload clutch between said ,brak a d aid motor and including a part rotatable with and axially displaceable with a part of said brake.

3. In a railroad highway crossing gate, a gate arm,-a gate-arm-actuating mechanism comprising a reversible driving motor connected to said arm for up and down propulsion, said motor including a stator and a rotor having a shaft, a centrifugal brake including rotatable parts carried by said shaft at one end, an overload clutch on the same end of said shaft positioned between said brake and said motor and having parts in common with said brake, and a slot to lock said shaft against rotation positioned .upon the opposite side of said rotor and including rotatable parts carried by said shaft.

4. In a railroad highway crossing gate, an arm pivoted for vertical movement between an hori- I zontal "warning" position and a vertical "clear position, counterbalancing means connected to said arm and arranged to exert a maximum counterbalancing force with said arm in the horizontal position and a minimum force with said arm inthe vertical position, means positively to drive said arm in both directions, and centrifugally' operated brake means operable at any time in mgrthepresence of excessive speed to limit the speed of descent of said arm.

5. In a railroad highway crossing gate, anarm pivoted for vertical movement between an horizontal warning position and a vertical "clear position, counterbalancing means connected to said arm and arranged to exert a maximum counterbalancing force with said am in the horizontal position and a minimum force with said am in the vertical position, means positively to drive said arm in both directions, and a combination overload release clutch and centrifugal brake to connect said driving means to said arm and to limit the speed of descent of said arm.

6. In a railroad highway crossing gate, an arm ,pivotedrfoi verticafinovement between a horizontal position and a minimum force with said arm in the vertical position, means positively to drive said arm in both directions, and centrifugally operated brake means to limit the speed of descent of said arm and including means to render itself inoperative in the movement of said arm from the horizontal to the vertical position.

7. In a railroad highway crossing gate, an arm pivoted for movement in a vertical plane, counterbalancing means to exert a minimum torque with said gate in the vertical position, driving means to lift said arm from the horizontal to the vertical position and to lower said arm, centrifugal brake means including a stationary drum and a shoe to limit the speed of descent of said arm and including means to cam said shoe from contact with said drum with said arm ascending.

8. In a railroad highway crossing gate, an arm pivoted for movement in a vertical plane, counterbalancing means to exert a minimum torque with said gate in the vertical position, driving means to lift said arrnfrom the horizontal to .substantially the vertical position and to drive said gate downwardly from the vertical position to approximately 45 from the horizontal with sufficient speed to insure its descent to the horizontal position by its own momentum and under the influence of gravity only.

9. In a railroad highway crossing gate, an arm pivoted for movement in a vertical plane, counterbalancing means to exert a minimum torque with said gate in the vertical position, driving means to lift said arm from the horizontal to substantially the vertical position and to drive said gate downwardly from the vertical position to approximately 45 from the horizontal with suflicient speed to insure its descent to the horizontal position by its own momentum and under the influence of gravity only, and centrifugal brake means to limit the speed of descent of said arm and including means, to render itself inoperative in the movement of said arm to the vertical position.

SAMUEL MISKEILY. 

